JP4751396B2 - roll - Google Patents

Abstract

A roll is supported at the middle thereof, for a paper, board or finishing machine is composed of two sections, a so-called inner shell (54′) and an outer shell (52′), supported by one another in the middle area of the roll (50′). The nominal stiffness of the manufacturing material of the inner shell (54′) of the roll is substantially greater than the nominal stiffness of the manufacturing material of the outer shell (52′) of the roll.

Description

  The present invention relates to a roll for a paper machine, a paperboard machine or a finishing machine. More particularly, the present invention relates to a composite roll supported at the center. Most preferably, the composite roll of the present invention is used as a calendar fly roll or spreader roll in a paper machine or paperboard machine. The present invention also relates to a new kind of roll supporting roll and a driving device for a roll in an excessive speed range.

  The above-mentioned roll is supported in the middle, and is mainly used as a lead roll, a spreader roll and a fly roll in the paper industry. They are characterized by different deflection characteristics than conventional rolls supported at the ends. Thus, for example, the length difference between the edge and the middle region of the fiber can be compensated by them, by bending the roll into a sag configuration in a direction away from the direction of the approach (spreader roll). Or you can guarantee that the web will not wrinkle.

One type of spreader roll is disclosed in US Pat. No. 6,099,077, in which the roll is formed by two concentric shells that are spaced apart from each other when in a resting state. That is, they are often referred to as inner shell and outer shell, and are incorporated in the middle part of the roll in the length direction. The inner shell includes a shaft journal that is rotatably mounted on the bearing. When a roll of the type described above is rotated in a paper machine or the like, either the machine fibers or the web, or both, impart some degree of deflection to the inner shell of the roll. However, as described above, the bending is not transmitted to the outer shell attached to the inner shell only around the middle portion of the roll, but tries to maintain its straight cylindrical shape. Depending solely on the stiffness of the outer shell, it can be kept straight during operation or can bend in the opposite direction in the direction of the line of sight of the inner shell. In both cases, the possibility of wrinkling the fiber or web is prevented. The inner shell of the prior art spreader roll is made of steel and the outer shell is made of fiber reinforced or fiber mat reinforced plastic. Examples of the outer shell material include epoxy / glass fiber, polyester / glass fiber, and epoxy / carbon fiber. In the prior art roll, the axial nominal stiffness of the inner shell is lower than that of the outer shell.

  Regarding the above-mentioned Patent Document 1, it is also worth noting that it relates to a composite spreader roll manufactured by, for example, a carbon fiber reinforced epoxy resin.

  Calendar fly rolls are discussed in Patent Documents 2 to 5, for example. These structures are very similar to the structure of the spreader roll described above, at least as far as relevant to the present invention.

  Furthermore, a configuration suitable to operate as both a spreader roll and a fly roll is discussed in the applicant's patent document 6, where the inner shell is conventional on a bearing with a machine frame structure. A roll mounted in an aspect is disclosed. The actual invention of this application is to support the outer shell at its end through an adjustable bearing arrangement on the machine frame structure in such a way that the direction and amount of deflection of the outer shell can be controlled. .

  The roll supported at the intermediate portion as described above is characterized by a relatively flexible outer shell and a relatively rigid inner shell. This property is brought about through the size and / or material selection between the inner shell and the outer shell.

  However, even if spreader rolls are used, some issues apply, especially with calendar fly rolls, a problem often encountered when using these rolls is the critical nominal frequency of the roll. When the outer shell of a composite roll is supported only by the inner shell, it is often supported only by the middle part of the roll, but the first critical nominal frequency of the roll is that the roll diameter is an existing fly roll Assuming that it is kept equal to the spreader roll, it stays relatively low. In practice, in order to be able to use a roll at a certain rotational speed, this means that it should be ensured that the rotational speed is not within the limit nominal frequency of the roll. In most cases, the rotational speed of the roll is kept below the critical nominal frequency (limit nominal frequency). In practice, in some applications where the rotational speed of the roll is likely to correspond to its critical nominal frequency, the only way to avoid it is to increase the diameter of the roll. However, this is usually not possible. This is because, for example, in a super calendar, there is no space for a roll having a diameter in such an order.

  That is, dimensional constraints are the most dominant issue. For example, calendar elevators and roll clearances must meet certain safety standards. The larger diameter of the roll necessarily changes the nip exit and entrance angles.

Another problem worth noting is that tension measurements cannot be performed, at least with some conventional spreader rolls. This is because when these rolls are used, the roll sag causes a moment to be applied to the attachment portion at the end of the roll, and this moment significantly disturbs the tension measurement. This type of roll is formed from a single cylinder, which in most cases is made of a composite material, the two ends being axially spaced from each other at both ends at the frame structure of a paper machine or paperboard machine. Above, is supported. One point can be regarded as a fixed point of the support, while the roll receives a radial force via the other point, this force being in the pushing or pulling direction, causing the roll to sag. The force is therefore directed at the device, whereby the roll is fixed to or supported by the frame structure. In addition to tension, the force / moment that hangs the roll is inevitably detected by a sensor for tension measurement, and the data from the sensor is no longer valid. That is, when this type of roll is used, the tension needs to be measured with another roll.
Finnish Patent Publication No. 72766 U.S. Pat. No. 4,692,971 US Pat. No. 5,438,920 WO-A1-9909829 WO-A1-9742375 Finnish Patent Application 20031384 EP-A2-0363887

  Accordingly, it is an object of the present invention to eliminate at least some of the problems of the prior art described above.

  A more extensive examination of the factors used to influence the nominal frequency of the roll revealed that the elastic properties of the roll have a relatively strong influence on the nominal frequency of the roll. Therefore, we can take advantage of its elastic properties to raise the critical nominal frequency of the roll to a significantly higher level, and in addition, such a material that does not require any restrictions on roll dimensional requirements. Alternatively, one can begin to investigate whether it is possible to produce a roll of multiple materials. The present invention has arrived at inner shell and outer shell rolls having different elastic properties.

  In a sense, similar types of rolls are discussed in US Pat. No. 6,057,096, but only a conventional roll consisting of several different layers is disclosed, suggesting a roll supported in the middle. Not. At least a portion of the layer is made from a composite material wound in at least two different directions. For example, in some cases, the innermost layer of the roll is wound at an angle of 75-90 degrees with respect to the axial direction, in other words, is wound approximately in the radial direction. The outermost layer of the roll is similarly wound at an angle of 0 to 35 degrees with respect to the axial direction. It is taught that the internal stress of a roll manufactured in this manner is a compressive stress in the radial direction, which does not cause interlayer cracks in the roll. Reference is also made to other effective properties such as control of axial stretching and elastic properties that meet the objectives presented in US Pat.

  In addition, the elasticity and vibration of the roll are instructed to each other at the middle portion of the roll, and the inner shell and outer shell of the roll are supported by the roll fixing device and the bearing at the end of the roll. The fact that the vibration at the end of the can be better controlled is also positively affected.

  In a preferred embodiment according to the invention, a fixing and supporting device for the roll is also used, whereby the outer shell of the roll can be deflected at the end relative to the inner shell and hangs down the roll. In this case, the power transmitted to the attachment portion by the drooping of the roll does not actually exist as compared with the prior art, and this enables the tension measurement on the roll to be performed.

  The features of the roll for a paper machine or paperboard machine or finishing machine according to the invention are characterized in that the roll is supported in the middle and consists of two sections, the so-called inner shell and outer shell, which are mutually connected to the roll. Supporting each other in the intermediate region, the nominal stiffness of the roll inner shell manufacturing material is significantly greater than the nominal stiffness of the roll outer shell manufacturing material.

  Other features of the roll according to the invention are indicated by the appended claims.

  For example, according to the present invention, a critical nominal frequency can be safely increased by using a roll supported by an intermediate portion even when a fly roll having a conventional size is used.

  The roll according to the present invention has a composite structure and can be used as a spreader roll or, for example, a super calender fly roll. This is because they can be significantly reduced in diameter without having to compromise other roll properties.

  The roll according to the invention can be operated in a supercritical region which means that the rotational speed of the roll is higher than its nominal frequency. Thus, the roll diameter is small and the roll is cheaper from both a material cost and manufacturing standpoint. Also, the roll can be replaced with a steel roll used in a conventional configuration from the viewpoint of its size.

  Supporting the end of the outer shell of the roll in the manner as disclosed in the present invention facilitates the use of the roll at supercritical speed.

  According to a preferred embodiment of the invention, the roll is applicable to the point of use where tension measurements are required in connection with the roll.

  Both adjustment of roll outer shell deflection and roll sag can be performed by adjustment device 118. Furthermore, the sag is always performed at the same level regardless of the amount of sag.

  The roll of the present invention will now be described in detail with reference to the accompanying drawings.

  FIG. 1 is a view showing a prior art composite roll 10 supported at an intermediate portion as disclosed in Patent Document 1. As shown in FIG. This consists of a composite inner shell 16 attached to the shaft journals 12 and 14 and an outer shell 20 which is likewise a composite structure and is attached to an intermediate portion 18 in the longitudinal direction of the inner shell. Conventionally, the typical structure of a roll supported by the middle part of the roll is that the outer end shell of the roll, more specifically, the outer shell of the roll is not supported by the inner shell, An annular space 22 is provided between the inner shells, for example, to allow the outer shell 16 to be kept straight even though the inner shell 16 hangs down, or to allow the outer shell 20 to hang down opposite to the inner shell 16. Yes. In a composite roll with an intermediate support, the inner shell and the outer shell are conventionally manufactured from the same material, where the inner shell is substantially thicker than the outer shell, thereby increasing the rigidity of the inner shell. Or the inner shell is made of steel and the outer shell is made of a composite material.

  The roll shown in FIG. 1 is supported in the middle, and in practice, for example, downward in the figure, when the web and / or fiber forces influence the roll through the outer shell 20 and when the roll is machine When supported by the shaft journals 12 and 14 via bearings on the frame, the inner shell 16 of the roll tends to hang down between the shaft journals 12 and 14. However, this sagging tendency is not transmitted to the outer shell 20. This is because the outer shell is supported by the inner shell only at a middle portion thereof, that is, a section where the direction of the inner shell is substantially the same as the direction of the shaft line 24 passing through the center line of the bearing.

  In this case, in addition to transmitting the web force to the inner shell, the outer shell hangs in the opposite direction, i.e., due to the action of the web force, hangs upward in the figure. This is because the edge portion of the outer shell is less rigid than the intermediate portion supported by the inner shell. In this case, the outer shell and the inner shell of the roll hang down in opposite directions. In such a structure, it is known that the straightness of the outer shell of the roll is targeted regardless of the sag (bow) of the inner shell.

  The problem with the above-described roll configuration in which the intermediate part is supported is, inter alia, that the critical nominal frequency of a roll in which such an intermediate part is supported is very low.

  FIG. 2 shows a preferred embodiment of the present invention, together with the support structure disclosed in detail in US Pat. No. 6,099,077, which is particularly suitable for use in connection with a roll according to the present invention. . In this support configuration, the inner shell of the roll is supported in the usual way by the frame structure of the roll, but the outer shell is not left free in the conventional manner, but preferably through the end. Are supported on the same frame structure so that the amount and direction of sag are controllable. Accordingly, the roll 50 ′ shown in FIG. 2 includes an outer shell 52 ′, an inner shell 54 ′, a shaft sleeve 56, and a shaft journal 66. The inner shell 54 ′ of the roll 50 ′ is rotatably supported by a fixed support structure 60 via a bearing 68. In this case, the outer end of the shaft journal 66 of the inner shell 54 ′ is not movable in the radial direction. It is. The shaft sleeve 56 of the outer shell 52 ′ is supported via a bearing 58 by a moving bearing housing 80. In this embodiment, the bearing housing 80 is supported by the support structure 60 via the guide 82 so that the end of the outer sleeve 52 ′ of the shaft sleeve 56 and roll 50 ′ can move in the direction defined by the guide 82. To. The position of the guide can also be rotated in a radial plane, in which case the direction of the outer shell hanging down can be controlled. In a similar manner, the guide can be provided with a stopper in a manner as described in Patent Document 6, for example, and the amount of deflection of the outer shell can be controlled by the stopper.

  In the configuration shown in FIG. 2, the inner and outer shells of the roll are not attached to each other, but the inner shell 54 ′, particularly the center line CL thereof, has a spherical portion (valve) 58 having an outer diameter substantially equal to the inner diameter of the outer shell 52 ′. Is provided. Preferably, the outer diameter of the sphere portion 58 is slightly larger than the inner diameter of the outer shell 52 ′, but the inner shell 54 ′ is pushed by the outer shell 52 ′ so that the sphere portion does not appear on the outer surface of the outer shell 52 ′. Is done. Other ways of joining the inner and outer shells together are, among other things, sizing and shrinking, or, as will be described later in connection with FIG. 3, they are already integrated in the part manufacturing stage when they are composite materials. It can also be structured.

  From the point of view of the present invention, the fundamental difference between the structure shown in FIG. 1 and this roll is that in the configuration of the present invention, the inner shell 54 'and the outer shell 52' of the roll In order to be able to optimize both frequencies, it is formed from distinctly different materials.

  The basis for optimal operation of the fly roll or the like is that the inner shell is substantially more rigid than the outer shell. The axial elastic modulus of the inner shell laminate should be at least 80 GPa, preferably 250 GPa. These values, however, are higher than those normally achievable with carbon fiber reinforced rolls. An elastic modulus value of 80-250 GPa is achieved by preparing an inner shell of carbon fiber that is very rigid by winding. Suitable for this purpose, the elastic modulus of some highly rigid carbon fibers, commonly referred to as tar or pitch fibers, is about 400 GPa in the fiber direction of the straight layer.

  More specifically, in principle, there are two types of carbon fibers, namely so-called PAN-based fibers and pitch-based fibers. For PAN-based fibers, the basic material is polyacrylonitrile, for pitch-based fibers, it is pitch, manufactured during oil refining, and mainly classified as garbage. Pitch-based fibers are usually referred to as tar or pitch fibers. Due to differences in both basic materials and manufacturing techniques, the elastic modulus of these pitch-based fibers is at most approximately twice that of PAN-based fibers. When these pitch fibers are wound in the axial direction when preparing a roll, it is possible to achieve an elastic modulus in the axial direction of 160-250 GPa. When the roll is manufactured from the materials described above in the manner described below, the deflection of the inner shell will be minimized and the outer diameter of today's super calender fly rolls can be achieved dynamically. Yes, this is a general requirement for the use of the above-mentioned rolls to replace the previously used steel fly rolls that have bearings and have other problems of their own.

  In other words, a roll according to the present invention has a main roll whose outer shell is 0 to 30 degrees in an axial view, for example, in the manner as shown in US Pat. No. 4,856,158, for example. In this case, the elastic modulus in the axial direction of the outer shell stack is approximately 30 to 80 GPa. In some cases, the outer shell can be made of several other suitable materials, such as a non-reinforced plastic material. The inner shell is correspondingly wound only with higher stiffness fibers, mainly in the axial direction of 0-30 degrees, in which case the axial elastic modulus of the inner shell stack is the axial elasticity of the outer shell stack. About 2 to 4 times the rate. Both shells have a layer wound more than (+/− 45 to +/− 85) in the circumferential direction to keep the shell in shape. Thus, the term “mainly axial” preferably means that more than 70% of the layer is wound using that axial angle.

Another way of comparing the various rolls or their parts and their properties with each other is to use the nominal stiffness in the axial direction of the stack as a comparison parameter, which is expressed as k _ax = E _ax / ρ, E _ax is the elastic modulus of the laminated tube or shell in the axial direction, ρ is the density of the tube or shell, and in the case of carbon fiber, it is on the order of 1550 kg / m ³ . By using the nominal stiffness as a comparison parameter, the nominal stiffness of the outer shell is k _ax = 0.035 to 0.055 GNm / kg, and the nominal stiffness of the inner shell is correspondingly k _ax = 0.055 to 0. .165 GNm / kg. However, the nominal stiffness of the inner shell should be k _ax = 0.10 to 0.15 GNm / kg for larger web thicknesses (6,5 m or more). If the corresponding nominal stiffness is calculated for steel for comparison purposes, the steel k _ax value is 0.026 GNm / kg, and the composite inner shell nominal stiffness is less than the steel inner shell. It turns out that it is 4-6 times compared.

  FIG. 3 illustrates another preferred embodiment of the present invention showing how the roll inner shell 54 "and outer shell 52" can be supported or interconnected to each other. The roll 50 "is manufactured, for example, in such a manner that the inner shell is first wound on a suitable core, followed by a manufacturing mode as disclosed in US Pat. No. 4,856,158. That is, two core pieces are placed on the finished inner shell in a manner that leaves a free area between them in the middle section of the roll, on which the roll is compounded When manufactured from material alone, a “ridge” is wound that binds the roll sections together.The core piece can be used if necessary, eg, consists of a material that breaks when cured. The thickness of the core piece shell necessarily corresponds to the radial dimension of the annular spacing between the inner and outer shells of the roll. Is realized such that the above-mentioned ridges for the purpose of binding the roll sections are wound together in the area between the core pieces and then the winding is extended to the entire length of the roll. Or it may consist of the same material as an outer shell, or may consist of another material suitable for the objective.

  FIG. 3 shows another alternative configuration for supporting the end of the roll, adapted to the situation where the end of the roll is more preferably supported. In this alternative configuration, the inner shell 54 "of the roll is supported via a bearing 42 and a bearing housing 44 so that its position can be adjusted on a paper machine or finisher or the like frame structure. Both ends of the inner shell 54 ″ of the roll 50 ″ are provided with end sleeves 38, to which the shaft journal 30 protruding through the space inside the shaft sleeve 30 of the outer shell 52 ″ is attached. It is done. Similarly, the shaft journal 40 is rotatably supported at the outer end portion by a bearing housing 44 via a bearing 42. The bearing housing 44 is supported by an adjusting device 36 designated as an adjusting screw. That is, the end of the inner shell 54 "can be transmitted radially to the end of the outer shell 52" by the adjustment device 36, which produces the desired sagging of the outer shell 52 ". Is supported on the frame structure of the production machine via a shaft sleeve 30 and a bearing 32.

  FIG. 4 is a perspective view of the most preferred configuration for the roll of the present invention with the intermediate portion supported. Although the illustrated support arrangement is most preferred for use in connection with a spreader roll, other uses associated with rolls that are suspended are inevitably possible. The illustrated roll support and drive arrangement includes a bearing bracket 100 that is attached to the frame structure of a paper machine or other manufacturing machine, and if this is necessarily a drive side issue, this bearing bracket includes: For example, a roll drive motor 102 is attached or supported. The roll shaft that functions as an extension of the inner shell of the roll (the roll may be structured as shown in FIG. 2 or FIG. 3) passes from the left through the hole in the center of the bearing bracket 100 and the drive motor 102. Extends to the clutch. The clutch itself may be of any known type. The roll shaft is supported by the bearing bracket 100 by means of a bearing, which allows a change in the direction of the roll shaft within a sufficient range. Similarly, in a manner known per se, attachment of the drive motor 102 to the clutch or drive motor 102 to the bearing bracket is such that the angle can be varied.

  Also worthy of mention in this regard, necessarily, the method of driving the roll may be a belt pulley configuration at the end of the roll on the shaft journal of the inner shell, in which case the drive motor is connected to the roll It can be mounted relatively freely on the side, above or below.

  The shaft sleeve, which functions as an extension of the outer shell of the roll, is located inside the ring 104, and its position is changed by changing the position of the ring 104 in which the bearing sleeve is mounted on the bearing 105. Adjustment is possible so that the sag can be adjusted. The illustrated support arrangement allows the roll to hang in virtually any desired direction. More specifically, the ring 104 is supported by two levers 106 and 108 disposed substantially symmetrically on both sides of the ring 104. One end of each of the levers 106 and 108 is rotatably attached to a rotatable disk 110 that is separately disposed in the bearing bracket. The other ends of the levers 106 and 108 are rotatably attached to the outer peripheral portion of the ring 104 via the protrusions 112 and 114. Due to the symmetrical fixing method of the levers 104, 106, the locus of the center point of the ring 104 is straight when the ring 104 moves laterally. The ring (in the embodiment shown in FIG. 4) is supported from below by a disk 110 via a spring device 116 (eg, a gas spring), one end of which is supported by the disk, and the other end is supported by a ring 104. Yes. When viewed from the spring means 116, on the opposite side of the ring 104, in order to move the ring 104 in the lateral direction or to actually allow adjustment of roll sag (in this embodiment, An adjustment screw 118 or similar device is placed between the ring 104 and the disk 110 (which is otherwise free). The actual adjustment procedure will be described in detail with reference to FIGS. 5a and 5b.

  The rotatable disk 110 described above represents a preferred embodiment of the present invention and allows adjustment of the direction of the roll's depending surface. The disk 110 is rotatably arranged by the side of the bearing bracket 100. For example, the disk 110 is arranged so that the cylindrical protrusion of the disk passes through the center hole of the bearing bracket and is inside the protrusion from the shaft of the roll. Mounted on the bearing. Rotating the disk 110 about the shaft is inevitably possible, for example, by placing a gearing at several suitable points on the disk and correspondingly a threaded rod associated with the bearing bracket. Yes, the end of the threaded rod is illustrated as a square foot 124, in which case the rotation of the threaded rod causes the disk 110 to rotate about the shaft. Along with the disk 110, the ring 104 that defines the sag surface of the roll also rotates. Also other types of rotating devices known per se can be used.

  Specifically, when viewed from the bearing bracket 100, the disk 110 is disposed on the roll side. Further, the levers 106 and 108, the spring device 116, and the adjusting device 118 described above are attached or supported rotatably on the roll side of the disc.

  FIG. 5a is a plan view of the roll support arrangement according to FIG. This figure shows a basic position where the bending of the roll has not yet begun, but the shaft sleeve of the outer shell is concentric with the roll shaft. In other words, in the illustrated example, the bearing portion 120 of the bearing bracket 100 is shown concentrically with the bearing 105 disposed inside the ring 104. The spring device 116 also functions in a “rest state” in a manner that pushes the ring 104 to the right, in which case the adjustment screw 118 is supported by the counter surface 122 in the ring 104. At this time, the spring device 116 removes all the clearance from the system and makes the structure rigid.

  FIG. 5 b shows the situation where the ring 104 has been moved to the left by the adjusting screw 118 against the spring device 116. Note that the center of the ring 104 remains at the same height regardless of the rotation of the levers 106 and 108. That is, the movement of the center occurs linearly.

  As described above, in addition to the opposite side of the ring 104 with respect to the spring device 116, the adjustment screw 118 can be located anywhere in relation to the ring 104. It is also possible to arrange the adjusting screw between the lever 106 or the lever 108 and the disk 110. The only essential element is that it is possible to adjust the position of the ring with the adjusting screw in the direction allowed by the spring device.

  The effect of the above-described structure is that both adjustment of the outer shell runout and roll sag can be performed by one adjustment device 118, for example, when compared to the prior art. In addition, the sag is always generated in the same plane regardless of the amount of sag.

  As indicated above, a completely new type of roll supported intermediate part has been developed, which can reduce or eliminate some of the problems and disadvantages characteristic of prior art rolls. In addition, although the roll by this invention is mainly shown as a calendar fly roll, this invention is applicable to all the places which can use the roll by which the intermediate part was supported like a spreader roll, for example. 2-5 only show a few configurations that support the roll ends, only these support / bearing configurations should be used in connection with the roll of the present invention. Is not meant, and other types of support configurations are also applicable. Naturally, a conventional roll comprising an outer shell whose end is not fully supported, as shown in FIG. 1, is also within the scope of the present invention. In the foregoing, the present invention has been described in terms of a most preferred stylized embodiment in terms of exemplary illustration. Therefore, it will be appreciated that the invention can depart significantly from the embodiments described above, while remaining within the scope of protection defined by the appended claims.

It is a figure which shows the composite roll of the prior art supported by the intermediate part as disclosed by patent document 1. FIG. It is a figure which shows the preferable Example of this invention with the selective structure of the fly roll currently disclosed by patent document 6 in detail. It is a figure which shows the other preferable Example of this invention with the selective structure of a fly roll as disclosed by patent document 6 as a prior art. FIG. 6 is a diagram showing another configuration for supporting a roll on which an intermediate portion is supported according to the present invention, particularly a configuration that is preferably used for a spreader roll. FIG. 5 shows the use of the support structure according to FIG. 4 to hang down a roll. FIG. 5 shows the use of the support structure according to FIG. 4 to hang down a roll.

Claims (14)

A roll (50 ') for a paper machine or a paperboard machine or finishing machine, comprising an inner shell (54', 54 ") and an outer shell (52 ', 52") supported by the longitudinal center of the inner shell. , 50 ")
The rigidity of the manufacturing material of the inner shell (54 ', 54 ") is larger than the rigidity of the manufacturing material of the outer shell (52', 52"),
The outer shell (52 ', 52 ") is supported at its ends on bearings (58; 32; 105) on a paper machine, paperboard machine or finishing machine or the like frame structure ,
An end of the inner shell (54 ', 54 ") is rotatably supported by a fixed support structure (60) via a bearing (68, 42) .   The axial elastic modulus of the manufacturing material of the inner shell (54 ', 54 ") is substantially higher than the axial elastic modulus of the manufacturing material of the outer shell (52', 52") of the roll. The roll according to 1.   The axial elastic modulus of the manufacturing material of the inner shell (54 ', 54 ") is 2 to 4 times the axial elastic modulus of the manufacturing material of the outer shell (52', 52") of the roll. Item 2. The roll according to Item 1.   The roll according to any one of claims 1 to 3, wherein the inner shell (54 ', 54 ") and / or the outer shell (52', 52") are made of a composite material.   The roll according to any one of claims 1 to 4, wherein the inner shell (54 ', 54 ") comprises a wound body of tar or pitch fibers.   The roll according to any one of claims 1 to 5, wherein the inner shell (54 ', 54 ") is wound up to an angle of 0 to 30 degrees mainly when viewed in the axial direction.   7. The outer shell (52 ′, 52 ″) is made of carbon fiber, glass fiber, or plastic, and has a rigidity of 0.035 to 0.055 GNm / kg according to claim 1. roll.   The roll according to any one of claims 1 to 7, wherein the outer shell (52 ', 52 ") is wound up to an angle of 0 to 30 degrees mainly when viewed in the axial direction.   The bearing arrangement (58; 32; 105) at the end of the outer shell is movable in a radial direction relative to the shaft of the inner shell (54 ', 54 "). The roll according to claim 1.   The direction of movement of the radial bearing arrangement (58; 32; 105) is guided by a guide (82) provided on a support structure (60) that supports the shaft journal (66) of the inner shell or the shaft journal of the inner shell. The roll according to claim 9, which is regulated by a lever (106, 108) provided on a bracket supporting (66).   The amount of radial movement of the bearing arrangement (58; 32; 105), i.e., roll sag, is regulated by an adjustment device (118) that adjusts the position of the ring (104) mounted on the bearing arrangement. The roll according to claim 9 or 10.   The roll according to claim 11, comprising a spring device (116) together with the adjusting device (118), wherein the spring device removes the clearance of the roll-down mechanism. The roll according to claim 12 , wherein the adjusting device (118) comprises at least one rotatable screw.   The roll of claim 13, wherein the spring device (116) comprises at least one gas spring.

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